US4811628A - Lockable differential gear - Google Patents

Lockable differential gear Download PDF

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Publication number
US4811628A
US4811628A US07/111,633 US11163387A US4811628A US 4811628 A US4811628 A US 4811628A US 11163387 A US11163387 A US 11163387A US 4811628 A US4811628 A US 4811628A
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US
United States
Prior art keywords
housing means
differential
lamellae
transmission housing
transmission
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Expired - Lifetime
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US07/111,633
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English (en)
Inventor
Gamjad Winkam
Manfred Lommerzheim
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Bayerische Motoren Werke AG
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Bayerische Motoren Werke AG
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Assigned to BAYERISCHE MOTOREN WERKE AKTIENGESELLSCHAFT reassignment BAYERISCHE MOTOREN WERKE AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: LOMMERZHEIM, MANFRED, WINKAM, GAMJAD
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/22—Arrangements for suppressing or influencing the differential action, e.g. locking devices using friction clutches or brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
    • F16H2048/082—Differential gearings with gears having orbital motion comprising bevel gears characterised by the arrangement of output shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H2048/204—Control of arrangements for suppressing differential actions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2071—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using three freewheel mechanism
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
    • F16H48/32—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using fluid pressure actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H48/40—Constructional details characterised by features of the rotating cases

Definitions

  • the present invention relates to lockable differential gears for motor vehicles with a transmission or gear housing and a differential housing rotatably supported therein as well as with a lamellae set arranged in the differential housing which is adapted to be acted upon from the outside with a locking force.
  • Such a differential gear is disclosed in the DE-OS No. 33 13 283.
  • a hydraulic piston displaceably arranged in the gear housing is rotatably supported by way of a radial bearing on a wheel output shaft.
  • the axle shaft gear is seated at the other end of the wheel output shaft protruding into the differential housing, secured by way of a thrust ring.
  • the lamellae set representing the differential locking means is provided, in turn, between the axle shaft gear and the differential housing.
  • the piston Upon actuation of the locking mechanism, the piston seeks to pull the output shaft toward the outside which thereby takes along the axle shaft gear by way of the thrust ring.
  • the axle shaft gear presses the lamellae set against a support wall of the differential housing and effects a friction-locking connection between the differential housing and the wheel output shaft.
  • a disadvantage of this prior art solution resides in that the force path during actuation of the differential locking mechanism leads by way of the radial bearing arranged between the hydraulic piston and the wheel output shaft.
  • the radial bearing must be dimensioned correspondingly large in order to withstand the loads.
  • this is not always desirable not only for cost reasons, but also for space reasons.
  • a further and much greater disadvantage exists with this prior art construction in that as a result of the transmitted torque the tooth pressure which exists between the differential bevel gear and the axle shaft gear, seeks to displace the axle shaft gear in the direction toward the lamellae set and therewith to lock the differential gear up to a certain degree. In other words, during normal driving operation, the prior art differential locking mechanism always exhibits a certain and undesired locking action.
  • a lamellae carrier is provided between the lamellae set and the wheel output shaft, which is non-rotatably seated on this shaft by way of a spline-tooth arrangement, but is axially displaceable on the shaft.
  • the axle shaft gear is held on the lamellae carrier by way of a further spline-tooth arrangement which axle shaft gear is again supported at the differential housing.
  • the lamellae set is again supported at the axle shaft gear whereby the latter further conducts the abutment force of the lamellae into the differential housing by way of the teeth of the differential bevel gears.
  • the disadvantage of this solution resides in that during the locking the differential housing together with its spur bevel gear is axially displaced slightly by reason of the force path.
  • the spur bevel gear meshes with the drive pinion with a very accurately adjusted tooth play. During the locking operation, this tooth play is therefore changed which may lead to jamming, distortions, and noise developments.
  • the underlying problems are solved according to the present invention in that the acted-upon lamellae set is supported at the gear of transmission housing by way of an axial bearing.
  • the locking force is therefore supported according to this invention against the gear or transmission housing by way of an axial bearing.
  • an axial bearing permits a considerably higher load capacity than the radial bearings mentioned in the prior art so that the bearing does not assume any unacceptable dimensions.
  • a transmission member is provided between the lamellae set and the axial bearing.
  • This transmission member is separate from the differential housing from a force point of view and can thus transmit the locking force to the transmission housing without influence on the differential housing.
  • the transmission member includes a circular ring which is slipped over an external guidance of the differential housing. The circular ring abuts with one end face at the axial bearing arranged at the transmission housing. The opposite side thereof passes over into fork-shaped arms which engage into the differential housing and cooperate with the lamellae set.
  • the axial bearing is located between a wheel output shaft and the gear or transmission housing.
  • a thrust ring is provided for this purpose between the lamellae set and the wheel output shaft which introduces the locking force into the wheel output shaft.
  • the thrust ring may thereby be provided ahead of the axle shaft gear so that the force path leads by way of the axle shaft gear.
  • the thrust ring is located to the rear of the axle shaft gear.
  • a lamellae carrier is preferably provided in this case which acts on the thrust ring.
  • the axle shaft gear remains free of loads in this construction during a locking operation.
  • a further appropriate embodiment of the present invention is characterized in that the axial bearing is located between the differential housing and the transmission housing.
  • the lamellae set acts on an abutment shoulder of the differential housing which further transmits the loads onto the axial bearing.
  • FIG. 1 is a partial cross-sectional view through a lockable differential gear with a transmission member engaging into the differential housing in accordance with the present invention
  • FIG. 2 is a partial cross-sectional view through a modified embodiment of a lockable differential gear in accordance with the present invention in which a thrust ring is seated on the wheel output shaft ahead of the axle shaft gear;
  • FIG. 3 is a partial cross-sectional view through a still further embodiment of a lockable transmission in accordance with the present invention, similar to FIG. 2, but with a thrust ring between the axle shaft gear and the lamellae set;
  • FIG. 4 is a partial cross-sectional view through still another embodiment of a lockable differential gear in accordance with the present invention in which the forces proceed inside of the differential housing during a locking operation.
  • FIG. 1 illustrates a lockable differential gear for motor vehicles with a gear or transmission housing 1 only illustrated in part, consisting of several partial sections not described in detail herein.
  • a differential housing 3 is rotatably supported in the transmission housing 1 by way of radial roller bearings 2.
  • An axis 20 generally designates thereby the main axis of the gear. Insofar as reference is made in the text herein without further identification to an axis, it is understood that it will always refer to the axis 20.
  • the differential housing 3 itself consists again of a differential cage and of a spur bevel gear 4 secured thereon which meshes with a drive pinion 5 schematically indicated.
  • Differential bevel gears 6 are provided in a known manner inside of the cage of the differential housing 3 whereby FIG.
  • the axle shaft gear 7 includes a forward toothed section meshing with the differential bevel gear 6; an offset, cylindrical shaft section 7a provided with axial grooves adjoins the forward toothed section.
  • the differential gear 3 is provided in its interior also with an axial grooved sections 3c coaxial the shaft section and disposed opposite thereto.
  • a lamellae set is arranged between these two sections 7a and 3c which is generally designated by reference numeral 11. It is built up of individual lamellae which are in driving connection alternately with the section 3c of the differential housing 3 or the section 7a of the axle shaft gear 7.
  • one type of the lamellae is provided at its outer circumferences with corresponding engaging slots whereas the other type of lamellae includes comparable slots at its inner circumference.
  • the lamellae of the lamellae set 11 may normally rotate relative to one another without or only with negligible resistance. However, if they are pressed against one another, they connect friction-lockingly the differential cage 3 with the axle shaft gear 7 and thus act as differential locking mechanism.
  • the pressing-together of the lamellae is effected by an annular piston 12 which is guided in the housing 1 and is adapted to be acted upon with pressure by way of a connecting nipple 13 and feed channels.
  • the pressure medium is hydraulic oil in this case.
  • the pressure connection between the annular piston 12 and the lamellae set 11 takes place by way of an axial thrust bearing 14 and a pressure or thrust plate 15 which includes pin-like projections 15a distributed along its circumference.
  • the pressure plate 15 engages by means of these pin-like projections 15a through the differential housing 3 and acts upon the lamellae set 11 by way of a further spacer plate 16.
  • a thrust ring 17 is also provided in the differential housing 3 at the oppositely disposed end of the lamellae set 11.
  • a transmission member generally designated by reference numeral 18 consists of a circular ring 18a with fork-like axial arms 18b formed-on at the circular ring 18a.
  • the transmission member 18 is displaceably arranged by means of its circular ring 18a on an outer guidance of the differential housing 3.
  • the outer guidance is thereby located on the side of the differential housing 3 opposite the lamellae set 11, i.e. at the height of the axial shaft gear 8 respectively of the wheel output shaft 10.
  • the transmission member 18 engages with its axial arms 18b through corresponding openings into the differential housing 3 and abuts with the arm ends at the thrust ring 17.
  • the other end of the transmission member 18 is supported at the transmission housing 1 by way of an axial bearing 19.
  • the differential locking mechanism is not effective during normal operation.
  • the differential gear maintains its differential function, i.e. it permits different numbers of rotation for the wheel output shafts 9 and 10.
  • pressure is supplied to the annular piston 12 by way of the connecting nipple 13.
  • the annular piston 12 moves in the axial direction toward the right.
  • the lamellae set 11 is pressed against the pressure or thrust ring 17 by way of the thrust bearing 14 as well as the thrust ring 15 and spacer plate 16.
  • the pressure plate 17, in turn, is supported at the transmission housing 1 by way of the transmission member 18 and the axial bearing 19.
  • the lamellae of the lamellae set 11 are pressed against one another in such a manner that a frictional connection will establish itself between the same and as a result thereof, the differential action is cancelled.
  • the locking action can thereby be increased continuously depending on the pressure.
  • a lamellae set 11 is coordinated to only one axle shaft gear, namely the axle shaft gear 7.
  • axle shaft gear 7 it is quite feasible without difficulty, to provide the same arrangement additionally on the opposite side. Two pressure connections for two separate hydraulic pressure lines would then merely be necessary. This is true analogously also for the other embodiments to be described hereinafter.
  • the embodiment according to FIG. 2 does not include a component comparable to the transmission member 18 according to FIG. 1.
  • the thrust ring 17 is supported in this embodiment at an annular shoulder 7b of the axle shaft gear 7.
  • the annular shoulder 7b is formed by the offset section 7a accommodating the lamellae and the toothed part, properly speaking, of the axle shaft gear 7, which is larger in diameter.
  • the axle shaft gear 7 again abuts with its forward section at a thrust ring 30, which is inserted into an annular groove on the wheel output shaft 9.
  • the wheel output shaft 9 itself includes at its end projecting out of the differential housing 3 a bearing seat 9a for the accommodation of an axial bearing 21.
  • the other bearing shell or cage of the axial bearing 21 is located in a correspondingly formed section of the transmission housing 1.
  • the lamellae set is acted upon with a locking force by way of the annular piston 12, it is supported at the transmission housing 1 by way of the thrust ring 17, the axle shaft gear 7, the thrust ring 20, the wheel output shaft 9, and the axial bearing 21. The forces are therefore conducted back to the transmission housing 1 by way of the wheel output shaft 9.
  • the embodiment according to FIG. 3 differs from that according to FIG. 2 in that, on the one hand, the thrust ring which is designated in this embodiment by reference numeral 22, is arranged behind the axle shaft gear 7. Additionally, the lamellae coordinated to the wheel output shaft 9 are not seated directly on the shaft, but on a lamellae carrier 23 interconnected there between.
  • the lamellae carrier 23a consists of a cylindrical tubular section 23 reduced in diameter which is adjoined in one piece by a radially outwardly extending side wall 23b. The side wall 23b thereby faces the axle shaft gear 7, however, without contacting the same.
  • the tubular section 23a of the lamellae carrier 23 is drivingly connected with the wheel output shaft by way of a spline-tooth connection and includes a further spline-tooth connection at its outer circumference for the engagement of the lamellae coordinated thereto. Additionally, the lamellae carrier is supported with its end face facing the axle shaft gear 7 at the thrust ring 22.
  • the axle shaft gear 7 itself is, as already mentioned, not acted upon by the lamellae carrier 23, instead it abuts at a support wall 24 which is connected with the differential housing 3. During the actuation of the annular piston the forces proceed similar as in FIG. 2 by way of the shank of the wheel output shaft 9 to the axial bearing 21. However, the axle shaft gear 7 is outside of the force-path owing to the thrust ring 22 which is displaced toward the inside.
  • the comparable axle shaft bearing designated therein by reference numeral 25, is provided between the guide neck 3a of the differential housing 3 and the transmission housing 1.
  • a thrust ring 17 is again connected behind the lamellae set 11; the thrust ring is supported in this embodiment at an abutment shoulder 3d of the differential housing 3.
  • the abutment force supplied by the annular piston 12 is introduced by way of the thrust ring 17 into the differential housing 3 and proceeds from there back by way of the axial bearing 25 to the transmission housing 1.
  • FIGS. 3 and 4 the guidance of the annular piston 12 is constructed in a different manner from that in FIGS. 1 and 2.
  • a corresponding ring-shaped recess is provided in each case in a housing lid 1b of the transmission housing 1, within which the annular piston 12 is guided.
  • the guidance is formed by the assembly of the transmission housing from a housing section 1a and a housing cover 1b. In this manner, the guidance can be machined in a simple manner into the housing cover 1b.
  • the housing cover 1b has a section reduced in diameter which forms an outer cylinder surface.
  • the counter-part namely, the radially outwardly disposed guide surface is machined as inner cylindrical surface into the housing section 1a. These two cylindrical surfaces are located opposite one another when the housing cover 1b is emplaced and form the guide cylinder for the annular piston 12 which results as annular space.

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US07/111,633 1986-10-24 1987-10-23 Lockable differential gear Expired - Lifetime US4811628A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3636175 1986-10-24
DE19863636175 DE3636175A1 (de) 1986-10-24 1986-10-24 Sperrbares ausgleichsgetriebe

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EP (1) EP0264579B1 (de)
DE (2) DE3636175A1 (de)
ES (1) ES2012476B3 (de)

Cited By (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4919008A (en) * 1988-02-10 1990-04-24 Eaton Corporation Differential smart clutch with gear reaction
US4950214A (en) * 1988-05-05 1990-08-21 Uni-Cardan Ag Differential drive
US4976667A (en) * 1988-02-10 1990-12-11 Eaton Corporation Differential clutch and lever actuation system therefor
US5086867A (en) * 1988-07-08 1992-02-11 Tochigifujisangyo Kabushiki Kaisha Power transmission apparatus
US5087228A (en) * 1987-06-24 1992-02-11 Sigvard Johansson Device to oppose relative rotational movement between two rotatable shafts
US5098360A (en) * 1988-12-26 1992-03-24 Tochigifujisangyo Kabushiki Kaisha Differential gear with limited slip and locking mechanism
US5133696A (en) * 1989-03-31 1992-07-28 Fuji Jukogyo Kabushiki Kaisha Differential for a power transmission system of a motor vehicle
US5148903A (en) * 1988-07-28 1992-09-22 Fuji Jukogyo Kabushiki Kaisha Power transmission system for a four-wheel drive motor vehicle
US5215506A (en) * 1991-02-06 1993-06-01 Nissan Motor Co., Ltd. Electronically controlled differential limiting system
US5234091A (en) * 1988-07-28 1993-08-10 Fuji Jukogyo Kabushiki Kaisha Power transmission system for a four-wheel drive motor vehicle
US5687824A (en) * 1994-09-21 1997-11-18 Nissan Motor Co., Ltd. Multi-plate frictional clutch structure
US5908096A (en) * 1996-05-21 1999-06-01 Aisin Aw Co., Ltd. Hydraulic servo unit for vehicular power transmission system
US5913397A (en) * 1996-09-05 1999-06-22 Jatco Corporation Clutch structure with piston having surface recessed from pressure surface for reducing stress concentration
US6007456A (en) * 1997-05-14 1999-12-28 Jatco Corporation Select-shock control apparatus and method for vehicular automatic transmission
GB2354563A (en) * 1999-08-20 2001-03-28 Zf Lenksysteme Gmbh Lockable differential
US6290623B1 (en) 1999-06-28 2001-09-18 Dana Corporation Removable support of motor vehicle differential side gear that facilitates machining
EP1143169A3 (de) * 2000-03-27 2002-01-16 Meritor Heavy Vehicle Systems, LLC Betätigungseinrichtung für eine Differentialsperre
US20020198076A1 (en) * 2001-06-19 2002-12-26 Mack Trucks, Inc. Enclosed axle differential lock mechanism
US20100009798A1 (en) * 2006-07-14 2010-01-14 Borgwarner Inc. Hydraulically actuated electronic limited slip differential for front wheel drive vehicles
US20110127135A1 (en) * 2008-12-16 2011-06-02 Eaton Corporation Idle-Able Auxiliary Drive System
US8840515B2 (en) 2009-12-09 2014-09-23 Zf Friedrichshafen Ag Motor vehicle transmission having a controllable differential
US20150167812A1 (en) * 2012-05-28 2015-06-18 Scania Cv Ab Driven axle gear for a motor vehicle
JP2020026870A (ja) * 2018-08-16 2020-02-20 日立建機株式会社 車両用アクスル装置
US10975234B2 (en) 2018-04-05 2021-04-13 Exxonmobil Chemical Patents Inc. Crosslinked rubber dispersion in thermoplastic vulcanizates
US20240019002A1 (en) * 2022-07-15 2024-01-18 Rivian Ip Holdings, Llc Integrated disconnect for drive unit
US20240157786A1 (en) * 2021-04-05 2024-05-16 Hitachi Construction Machinery Co., Ltd. Vehicular Axle Device

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EP0393041B1 (de) * 1987-09-05 1991-08-21 ZF FRIEDRICHSHAFEN Aktiengesellschaft Differentialgetriebe mit einer lamellenkupplung als sperrkupplung
EP0414086B1 (de) * 1989-08-21 1993-10-13 Gkn Automotive Aktiengesellschaft Sperrbares Differentialgetriebe
US5007886A (en) * 1989-12-26 1991-04-16 Eaton Corporation Limited slip differential
DE10140358C2 (de) * 2001-08-17 2003-07-10 Infineon Technologies Ag Telefonsystem mit Stromregelung im Konstantstrombereich
WO2008008705A2 (en) * 2006-07-14 2008-01-17 Borgwarner Inc. Limited slip differential

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US3460404A (en) * 1965-09-29 1969-08-12 Leopold F Schmid Braking devices for differential gears of motor vehicles
DE1934340A1 (de) * 1969-07-07 1971-01-28 Schmidt Dipl Ing Karl Heinz Schaltbare Sperre fuer Kegelrad-Ausgleichgetriebe von Kraftfahrzeugen
GB1290542A (de) * 1968-10-29 1972-09-27
US3894446A (en) * 1974-06-03 1975-07-15 Twin Disc Inc Power transmission having friction clutch bias differential with automatic clutch release
US3915267A (en) * 1973-08-02 1975-10-28 Dana Corp Differential and braking assembly
US3974717A (en) * 1974-12-19 1976-08-17 Allis-Chalmers Corporation Four pinion differential
FR2434969A1 (fr) * 1978-08-30 1980-03-28 Bardot Michel Differentiel a glissement auto-controle
EP0063432A1 (de) * 1981-04-15 1982-10-27 Eaton Corporation Gesteuertes Ausgleichgetriebe
DE3313283A1 (de) * 1983-04-13 1984-10-25 Daimler-Benz Ag, 7000 Stuttgart Sperrdifferential mit einer in einem differentialgetriebegehaeuse angeordneten sperrkupplung, die von einem in einem achsgehaeuse angeordneten aeusseren stellglied der axialkolben-zylinder-bauart betaetigt wird
DE3444843A1 (de) * 1984-12-08 1986-06-19 Bayerische Motoren Werke AG, 8000 München Sperrbares ausgleichsgetriebe fuer kraftfahrzeuge
US4627513A (en) * 1983-05-19 1986-12-09 Dr. Ing H.C.F. Porsche Ag Intermediate differential for a vehicle including a spur gear/planetary gear arrangement
US4644823A (en) * 1982-04-03 1987-02-24 Dr. Ing. H.C.F. Porsche Aktiengesellschaft Differential gear
US4679463A (en) * 1984-08-31 1987-07-14 Nissan Motor Co., Ltd. Limited slip differential
US4730514A (en) * 1985-04-22 1988-03-15 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Differential speed limiting device mechanism

Patent Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3460404A (en) * 1965-09-29 1969-08-12 Leopold F Schmid Braking devices for differential gears of motor vehicles
GB1290542A (de) * 1968-10-29 1972-09-27
DE1934340A1 (de) * 1969-07-07 1971-01-28 Schmidt Dipl Ing Karl Heinz Schaltbare Sperre fuer Kegelrad-Ausgleichgetriebe von Kraftfahrzeugen
US3915267A (en) * 1973-08-02 1975-10-28 Dana Corp Differential and braking assembly
US3894446A (en) * 1974-06-03 1975-07-15 Twin Disc Inc Power transmission having friction clutch bias differential with automatic clutch release
US3974717A (en) * 1974-12-19 1976-08-17 Allis-Chalmers Corporation Four pinion differential
FR2434969A1 (fr) * 1978-08-30 1980-03-28 Bardot Michel Differentiel a glissement auto-controle
EP0063432A1 (de) * 1981-04-15 1982-10-27 Eaton Corporation Gesteuertes Ausgleichgetriebe
US4644823A (en) * 1982-04-03 1987-02-24 Dr. Ing. H.C.F. Porsche Aktiengesellschaft Differential gear
DE3313283A1 (de) * 1983-04-13 1984-10-25 Daimler-Benz Ag, 7000 Stuttgart Sperrdifferential mit einer in einem differentialgetriebegehaeuse angeordneten sperrkupplung, die von einem in einem achsgehaeuse angeordneten aeusseren stellglied der axialkolben-zylinder-bauart betaetigt wird
US4627513A (en) * 1983-05-19 1986-12-09 Dr. Ing H.C.F. Porsche Ag Intermediate differential for a vehicle including a spur gear/planetary gear arrangement
US4679463A (en) * 1984-08-31 1987-07-14 Nissan Motor Co., Ltd. Limited slip differential
DE3444843A1 (de) * 1984-12-08 1986-06-19 Bayerische Motoren Werke AG, 8000 München Sperrbares ausgleichsgetriebe fuer kraftfahrzeuge
EP0185247A2 (de) * 1984-12-08 1986-06-25 Bayerische Motoren Werke Aktiengesellschaft, Patentabteilung AJ-3 Sperrbares Ausgleichsgetriebe für Kraftfahrzeuge
US4730514A (en) * 1985-04-22 1988-03-15 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Differential speed limiting device mechanism

Cited By (37)

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US5087228A (en) * 1987-06-24 1992-02-11 Sigvard Johansson Device to oppose relative rotational movement between two rotatable shafts
US4976667A (en) * 1988-02-10 1990-12-11 Eaton Corporation Differential clutch and lever actuation system therefor
US4919008A (en) * 1988-02-10 1990-04-24 Eaton Corporation Differential smart clutch with gear reaction
US4950214A (en) * 1988-05-05 1990-08-21 Uni-Cardan Ag Differential drive
US5086867A (en) * 1988-07-08 1992-02-11 Tochigifujisangyo Kabushiki Kaisha Power transmission apparatus
US5148903A (en) * 1988-07-28 1992-09-22 Fuji Jukogyo Kabushiki Kaisha Power transmission system for a four-wheel drive motor vehicle
US5234091A (en) * 1988-07-28 1993-08-10 Fuji Jukogyo Kabushiki Kaisha Power transmission system for a four-wheel drive motor vehicle
US5098360A (en) * 1988-12-26 1992-03-24 Tochigifujisangyo Kabushiki Kaisha Differential gear with limited slip and locking mechanism
US5125876A (en) * 1988-12-26 1992-06-30 Tochigifujisangyo Kabushiki Kaisha Differential gear with limited slip and lockup clutches
US5133696A (en) * 1989-03-31 1992-07-28 Fuji Jukogyo Kabushiki Kaisha Differential for a power transmission system of a motor vehicle
US5215506A (en) * 1991-02-06 1993-06-01 Nissan Motor Co., Ltd. Electronically controlled differential limiting system
US5687824A (en) * 1994-09-21 1997-11-18 Nissan Motor Co., Ltd. Multi-plate frictional clutch structure
US5908096A (en) * 1996-05-21 1999-06-01 Aisin Aw Co., Ltd. Hydraulic servo unit for vehicular power transmission system
US5913397A (en) * 1996-09-05 1999-06-22 Jatco Corporation Clutch structure with piston having surface recessed from pressure surface for reducing stress concentration
US6007456A (en) * 1997-05-14 1999-12-28 Jatco Corporation Select-shock control apparatus and method for vehicular automatic transmission
US6290623B1 (en) 1999-06-28 2001-09-18 Dana Corporation Removable support of motor vehicle differential side gear that facilitates machining
GB2354563A (en) * 1999-08-20 2001-03-28 Zf Lenksysteme Gmbh Lockable differential
GB2354563B (en) * 1999-08-20 2003-06-04 Zf Lenksysteme Gmbh Lockable differential gear
EP1143169A3 (de) * 2000-03-27 2002-01-16 Meritor Heavy Vehicle Systems, LLC Betätigungseinrichtung für eine Differentialsperre
US6508734B2 (en) 2000-03-27 2003-01-21 Meritor Heavy Vehicle Systems, Llc Differential lock actuator
US20020198076A1 (en) * 2001-06-19 2002-12-26 Mack Trucks, Inc. Enclosed axle differential lock mechanism
US20040248692A1 (en) * 2001-06-19 2004-12-09 Mack Trucks, Inc. Enclosed axle differential lock mechanism
US20100009798A1 (en) * 2006-07-14 2010-01-14 Borgwarner Inc. Hydraulically actuated electronic limited slip differential for front wheel drive vehicles
US20110127135A1 (en) * 2008-12-16 2011-06-02 Eaton Corporation Idle-Able Auxiliary Drive System
US8596436B2 (en) * 2008-12-16 2013-12-03 Eaton Corporation Idle-able auxiliary drive system
US8840515B2 (en) 2009-12-09 2014-09-23 Zf Friedrichshafen Ag Motor vehicle transmission having a controllable differential
US20150167812A1 (en) * 2012-05-28 2015-06-18 Scania Cv Ab Driven axle gear for a motor vehicle
US9709149B2 (en) * 2012-05-28 2017-07-18 Scania Cv Ab Driven axle gear for a motor vehicle
US10975234B2 (en) 2018-04-05 2021-04-13 Exxonmobil Chemical Patents Inc. Crosslinked rubber dispersion in thermoplastic vulcanizates
CN111788412A (zh) * 2018-08-16 2020-10-16 日立建机株式会社 车辆用车轴装置
JP2020026870A (ja) * 2018-08-16 2020-02-20 日立建機株式会社 車両用アクスル装置
US11143281B2 (en) * 2018-08-16 2021-10-12 Hitachi Construction Machinery Co., Ltd. Vehicle axle device
CN111788412B (zh) * 2018-08-16 2023-09-26 日立建机株式会社 车辆用车轴装置
US20240157786A1 (en) * 2021-04-05 2024-05-16 Hitachi Construction Machinery Co., Ltd. Vehicular Axle Device
US12090841B2 (en) * 2021-04-05 2024-09-17 Hitachi Construction Machinery Co., Ltd Vehicular axle device
US20240019002A1 (en) * 2022-07-15 2024-01-18 Rivian Ip Holdings, Llc Integrated disconnect for drive unit
US11940022B2 (en) * 2022-07-15 2024-03-26 Rivian Ip Holdings, Llc Integrated disconnect for drive unit

Also Published As

Publication number Publication date
EP0264579B1 (de) 1990-01-03
DE3761334D1 (de) 1990-02-08
ES2012476B3 (es) 1990-04-01
EP0264579A1 (de) 1988-04-27
DE3636175A1 (de) 1988-04-28

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